Crusher



Aug. 17, 1943. R. E. BROWNING CRUSHER 4 Sheet-Sheet 1 Filed Feb. 26 1941 INVENI'OR R-E.BROWNING BY ATTOB NE S FD m:

CRUSHER Aug. 17, 1943.

Filed Feb. 26, 1941 4 Sheets-Sheet 2 E; 72? 51 V E 39 '7 8E 43 3 5 49 INVENTOR FIGA naanowmue 1943' R. E. BROWNING 2,326,750

CRUSHER Filed F eb. 26, 1941 4 Sheets-Sheet s INVEN'IOR R.E.BROWNING @Mwff 1943- R. E. BROWNING 2,326,750

CRUSHER Filed Feb. 26, 1941 4 Sheets-Sheet 4 INVENTQR R.E.BROWNING AT T0 BN15 5 ponent of motion.

Patented Aug. 17, 1943 v CBUSHER Raymond E. Browning, Verdun, Quebec, Canada,

assignor to Frederick Quebec, Canada A; Peacock, Montreal,

cation rebruaryzc, 1941, Serial No, 33 0- i In Canada March 27, 1940 v V v 11 Claims. (01. 83-10) This invention relates to'impi'ovements in gyratory crushers of the type set forth in my original application Serial No. 282,227, filed June 20, 1939;.

the present application being a continuation-in part, of said original application. 7 i

In its. preferred embodiment my improved crusher comprises a. frame, an, outer annular crushing member of substantially ccnicalform mounted on said frame so that its central axis is vertical, an inner annular crushing member of substantially conical form located within said outer member, a support on which the inner member is rotatably supported in a tilted position so that the central axis of said inner member is inclined to intersect the centralaxis of the outer member at a focal point located below said inner member and means for gyrating the inner member so that its central axis describes a invertedcone having its apex at said focal :point.

This type 'of crusher is distinguished by a novel crushing action in'that the portion of the-inner member which is making a crushing stroke in the direction of the outer member approaches said outer member with substantial downward comtion onsaid material in one pass through the Reduction ratios as high-as 1 to v crushing zone.

Under these circumstances the crushable material interposed between the'two ployedin rock'crushing operations, such, for ex- I ample, as the shaker Screens, crushingroll's','ball' 36and 1 to 48 have actually been obtainedin practice with crushersdesigned in accordance withthisinventicn; These high reduction ratios are made possible by designing the crusher so that, during a crushing stroke of the inner meme ber,- the downward component of motion of. said member, especially at the discharge end of the crushing Zone,'is suitably proportioned with respect to the crushing motion-ofsaid member in the direction of the outer memberh Whenthe Y crushing approach which the-lowest crushing point on the inner member nakes toward-the outer member is suitably proportioned with ref.- erence to the downwardmotion of said point, .it

is possible to provide a crusher in which the crushing surfaces can be brought closerftogethe'r with crushable material interposed betweenthem than is the casewith any ofthe crusliersnow onthemarket. T M

Owing to the exceptionallyhighratio of reduc tion which it performs I on crushable material on one pass through the-crushingzone, my improved gcrusher makes it possible to dispense with considerable intermediate equipment commonly emmills, conveyors anddust fansi V A furtheradvantage of my improved crusher is that it lends itself to the use jofanti-friction bearings for mounting all rotating parts so that the power requiredto-operate the crusher is con siderably reduced as comparedwithv prevailing standards, T

A further feature: resides inr the provision 'of simple and efficient-means for adjusting'therelative setting of. the outer and'inner crushing elements to produce a'c'rushed product. of the decylindrical dust shields and other similar accessories which have'heretofore beenemploye'd for this purpose. 7

A stilliurther feature resides in the provision of novel means whereby an eificient oil-seal is provided between the interior load bearing and,

lubricated surfaces of the 'crusherand the ace: rior dust bearing air and mechanism;

A further feature of; the invention resides the i a provision of adjusting means incorporated in the crusheriorchanging the obliquity of thegyrat in axis of the inner-crusher member with'reference to the axis ofthe outercrushing'membe ri 7 Another advantage ofthe unique crushing-ac tion of my improvedcrusher is that it eliminates 1 Y attrition andtherebymaterially reduces-the wear on the crushing surfaces.

Proceeding-nowto a more detailed description of the invention reference will behaclto the accompanying drawings, whereint Fig. l is a vertical sectional plete crusher assembly.

Fig.2 is a perspective view showing the threaded segments and clamping members employed'ffor 1 adjusting the mantle element of the crusher.

Fig, 3 is an enlarged fragmentary sectional view illustrating the mounting of the cone elementand the shaft by. which the cone elem ent isgyrat'ed with reference to the mantle element.

' Fig. 4'is an enlarged fragmentary sectional view showing the mechanism providedfor varying the g obliquity of the. gyrating axis'of the cone element.

Fig. 5 is an enlarged'fragmentary sectional view of a portion of the mechanismjillustrated iiiFig- V urea 1 and 3.:

Q 1 Fig. c is a view partly in sideelevation and View of my com- :the inner end'of a count rshaf t extends, said opening heing passage 38, to an oil tank (not shown) to the suction side of the pump is connected.

crusher.

Fig. '1 is a plan view of the shaft shown in Fig. 6.

Fig. 8 is a plan view of an adapter sleeve.

Fig. 9 is a vertical sectional view of the adapter sleeve shown in Fig. 8. c

Fig. 10 is a plan view of a washer. Fig. 11 is a vertical sectional view of the easier shown in Fig. 10.

Fig; 12 is a plan view of nut employed for securing the adapter sleeve on the shaft.

Fig. 13 is Figure 12. I g V Figs, 14 and 17 diagrammatic views illustrating the crushing action characteristic of improved crusher. V

Figures 15 and 16 are diagrammatic views illustrating the effect of varying the location of the crusher is 'gyrated.

focal point about which the cone element of the Referring moreparticularly to the' drawin 's; {idesignates a cylindrical'frame provided withe square base 5 which rests flatly onthero' .1ndation 6; A cylindrical sleeve l is centered and.

a sectional low of the not shown in face 44 is le'ssthan that of surface 43..

' partly in vertical section of the main shaft of the ing cylindrical extension 42. The extension 42:

is force-fitted in the upper portion of sleeve '5 so that the shoulder 4| bears on the upper end of the sleeve and is bolted thereto as indicated at Ma. It will also be noted that'the lower end of 7 extension 42 bears against the flange is of seat ring 16 and assists in retaining said ring in place. Sphere head 49 has two annular spherical su3- faces 63 and as formed thereon so that both surfaces have a common focus or center but dif-' ferent radii. As clearly shown in the drawings the area of surface 44 is considerably greater than the area of surface 43 but the radius of sur- The two surfaces 3 and M are separated by a cylindrical portion 4! (see Fig. 5 on which an oil seal ring 48 is shrunk fitted. An annular channel 49 is formed in the sphere head between the spherical at the lower end of sleeve 1 and rests on the cyopening I V The inner cone -l2aof'bearing I2 is a force fit on the upper end of hub? and bears against the upper side of hub flange 55. The outer cone 12b lindrical extension !;3of a cover i4 closing said of bearingl! is a force fit in a seat ring 16 and bearsagainst an inwardly directed flangeli at the uppered ge of said ring. A flange 18 projects outwardly from'the lower portion of ring I; and bears on a shoulder i9 c t-sleeve i. i5 is bolted-in place'as indicated'at Eta Abevelgear 2i isiastenicd to the underside of gear hub flange l5 bjboltsfi. This gear meshes with a driving-bevel pinien ifi fi cdtc The coini- 'tershaft is journalled in the countershaft'hcusing 2-5 by means of anti-friction bearings 26 and 21. Housing is fitted in the bcre 23 of frame action 9 and is securedin-place hy bolts 25.

The'outer end of housing 25Lis provideduiith a removable bearing cover 311. provided with a cen- ..A spiral gear 32 is to counts shaft 24 adjacent hearin", 26. This gear mesheswith, .a spiraLge-ar 33 fixed toa. Shaft .35 which operates an oil pump (not shown). The discharge side of the pump is connected to a central vertical oil passage 35 formed bottom cover. H of sleeve I; The oover H is also-providedwith a horizontal oil passage 3% and oil collecting sump--37. The oil which is delivered to surhp 3] as hereinafter descrihe'dis returned, th ougn which This sphere h ad is iorrnedwith "75 26 and Z1 and thespiral gears 32 and 33.

surface 44 and the annular portion 46 and serves as a collecting channel for oil draining from the surface 44. The oil collecting in channel 59 passes through drain holes 56 into the interior of -sleeve1.

The spherical surface 34 is-interrupted by an annular oil groove 5| located substantiallyxrnidway between the upper and lower edges. of said surface. Adjacent the'mouth of thezgroove the side walls thereof arecurved as indicated at 510. (Fig. 5) so that oil supplied to said groove will be distributed, according to a wellknown oil fee:

thrust principle, to form a lubricating: film. be

tween the surface 44 and the opposing spherically curved surfmes 52 of thehead liner. 53 hereim.

after referred to. Oil under pressure issupplied to 'oil groove through oilpassage's 35 and'36' in oil filmcontact therewith. When the .crusher is in operation this liner serves to distribute the enormous concentrated rock crushing forces over thellargel spherical surface 44 Liner 53 (see Fig.3) is provided with a cylindrical par-f tion 64 located'betw'een a flat top surface 65 and a'bevelled outer side surface 66. Thecylindrh cal portion 64 ls' forcefitted in a cylindrical. portioriG'l of a substantiallyconical head car rier 68 so that the liner surfaces 65.. and are brought" in flat contact with complem-cntaryfiat and beveled surfaces 69 and '19 of the carrier.

Head carrier 68 is bolted to liner 53 sis-indicat ed at"?! and is provided with a skirt portion 72 having a spherically curved surface 12a which,

conforms to and is disposed inclose proximity -to the spherical curved'surf-ace '43 ofsphere head 49. 'Ihe inner'sldeof skirt-portion I2 is shaped so thatit forms, in conjunction withthesphcre head 40, a channel or recesslfl which accommo- 7 dates the oil seal-ring 48 with sufficient clear ance to permit the liner and carrier elements of the crusher head asSemblyto be rnoved through: a complete gfi'ration or-istrol rewithout coming in contact' with 'said ring,

A conical crushing head 14 of manganesestecl or other wear resisting material is fitted on head carrier 63 in machine groundmatching contacttherewith and isIsecured'to-the carrier'by'the head fastening screw l5.- The'head of screw bears against thebottom' wall of a recess lfiprovided in the head 74.- A rubber disc'l'l is fitted in recess lfito excludedust and'prevent abrasion The obliquely inclined central axis- 34d of shaft extension 79 meets the central' vertical axis 34c of the main shaft se'ctionBll at :the focal point 8!.

and the'liner 53.

Shaft extension 79 comprises a'taper portion 19d and a threaded end 1919. 1 An adapter sleeve 82 (Figs. 1 and 3) is fitted on the taper portion 19a. The axis of the bore of sleeve fiicoin cides with the axis 34d of shaft extension 79,

The axis of the outer diameter of sleeve 82 is indicated at 4 1 and is obliquely-inclined with respect to the axis 34d, thetwo" axes meetin at the aforesaid focal point 8i whichis located on the vertical axis 3% of shaft'section 8B and which also constitutes the centre of curvature of the spherical surfaces 43 and. Sleeve 82 is turnable to various adjusted positions about taper portion 19a of shaft extension 79 and is secured in adjusted position by a pin 84 which is fixed in a portion of the shaft so that it may be selectively engaged in notches 85 provided in thelower end'of said sleeve. 'Shims 89 areinterposed between the upper end of sleeve82 and the cylindrical extension 81 of a'nut 88 which is fitted on the threaded end 'leb of shaft extension 80. Nut 88 is formed with a spherical seat 8Q and is locked in place by a locking wire 88a. As shown more clearly in 12 wire 83a is seated gagement with fithe taper shaft :portion "80." Threaded-holes 98 are also provided 'inhead carrier -Ei8'-to facilitate dismantling of the-force fitbetween the hear carrierfand the cone 93 as betweenthe head carrier.

well as the force fit The lower portion of shaft sectiontil slid- 'ablyfitted in bevel gear hubifi andis positively rotated with said hub by rneans of the key 99.;

That portion of shaft section 8i! whichjlies between I the oblique shaft extension 19.. and ;the

upper endof hub I!) is centered in'sphereh'ead v tfi by 1 means: of. an. anti-friction bearing; I108;

(Figs; 1 and 3) .:The outer cone :18! of bearing 20 is force fitted in. a cylindricalflportion 162 of sphere head 14D .and'ibears against a fiange lflii overhanging. said cylindrical portion; The. in;

ner cone i lfld of bearing 190 is force fitted n shaft sectionfiq and bears against the shaft .flange. IE5, j The j gyratory. head. shaft, comprising mainfl shaft section at and oblique extension E9, is provided with afull length oil passageili'l through whichsome. of the oil pumped to thepreviously.

mentioned oil'tpas'sage .35 in cover] 4.; is forced over the upper end ofithe shaftytoprovide for the lubrication necessary for the shaft-bearings 92 and IE9 and the hub bearing l2 and fl. Thein nut groove 88b and has a bent endv 88c extending inwardly through one of the radial openings 88d, The bent end 880 (see Figs. 12 and '13) is received in one of a series of notches 88c provided in the threaded shaft portion'lBb;

. I he upper end of the adapter sleeve-"on which is supported on the flat top'surface 65 o'f'liner 53. The inner. cone' 93a of bearing 92 isslip fitted on the adapter sleeve 82 so that sufficient pressure is exerted against the inner diameter of the cone when sleeve 82 is forced down the taper shaft portion 79a by pressure applied by nut v The cylindrical extension 87-01" nut 83 is encircled by a washer-95 provided with a spherical surface 98 (Figs 1, 3 and 4,) in matching contact with the spherical seat SQ, The outerrdiameter of washer 95 isconcentric 'with'axis 44' while the lower face of-said Washer lies on'a plane perpendicular to said axis and is in normal contact with the thrust fa'ce93 of cone'93a (Fig. 4). with the axis 34d of theobliquely inclined 'shaft extension 19. A pin 9'| is rigidly'fixed in washer' 95 and is used to locate the washer circumferentially by being inserted in one of a series "ed toreceive threaded tools employed in with upper end of oil. passage Hi1 ispartially blocked by a plug [68 (Fig.7 6) provided with a restricted orifice I69.

Abullring lit isfsupportedon and definitely '1 v located by the frame 4. Thecontacting surfaces k 1 of the bull ring and frame are carefully formed to ensure maximum efficiency whenjthe crusher is in operation. In this connection it will gbe noted-that the bull ring contacting surface of frame 4 is contoured so that it comprises a-hori zontal surface; HI and a-radial-curve H2 merging with a tangential projection H3 forming'an. inverted; frustum of {cone having an inclined angletof approximately degrees; ,The horiezontal surface Hi, intersects apoiriton thecurve H21about-20- degrees'from the vertical. The frame'engaging surface of the bull ringis formed witha radialcurve l ltmatching the radial curve H2 and with a tangential projection 55 matchin the tangential projection I-l3.- The curve 5311GT the bull ring'merges with a horizontal tangential projection 1 t5, which is V normally spaced above the'horizontal surface I ll.

The bull ring I H} is preferably made-of steel:

and must be of very strong construction; Asindicated by. dotted lines H8, itis mainly a frus turn of cone form having upper and lower accurately bored cylindrical bore sections H9 and E29. Freely fittedin the bull ring; is the cylindrical portion i2l of a mantle carrier I22. This cylindrical portion of the mantle carrier is threaded at its outer periphery so as to leave smooth full diameter band portions 123 and I24 The bore of washer is concentric.

above and below the threaded portion E25. The lowerbandportion H4 is provided with an annular. groove 126 in which a suitable formqof grease packing i2? is held-so thatsaid packing makes wiping contact with the lower cylindrical bore section] I29 of, thebull ring,

Four threaded segments ['29 arexarr-anged the bull ring for threaded engagementwith'the threaded :portion 125 of the lmantle carrier. Each segment I29 is providediwitha machined horizontal'bottomisurface 13d and'is accurately, I V bevelled asrindicatedfat lfil to match the engag ing bevelled surface l32 of the bull ring. The

drawing the sleeve 82' from: its z'wedging.; .ene

segments lifl are supported by {our clamps- I33 disposed inacontact with the bottom surfac s I30,

- each clamp having two. threaded boss. extensions Iiilto provide amplethreadedlengagement with heavy cap screws through boss extensions I36 of the hunt n I extendin downw rd y The force exertedby the head of each can Screw I35 is imposed against; metal washer I31 an rubber canvas washerIBS supported by one of r the boss extensions I36.

-The bull ring is also provided witha boss I39a having a bore I391) in which a-pinion shaft I39 1 is slidably fitted. A pinion I40 is fitted on the upper portion of said'shaft" and rests on boss 1390.. A bushingMI .is fitted in pinion I40 to provide a bearing fit between the pinion and the pinion shaft. Pinion I. isprovided with a sleeve extension I42 having a topthreaded opening I43 intowhich a plug I44 is screwed- When:

this plug is removed an eye bolt maybe: screwed into the threaded hole I45 at the upper endaof.

shaft I39 to remove shaft I35 withoutdisturbing the pinion.

The -mantle carrier I22is provided with a 'hopper' forming portion I41 and with a cylin' vided with a machined surface I54 in sliding contact with a machined-surface I55 provided at the inner side of the cylindrical cover supporting portion Ids The outer flange I53 of the coverring is also provided with a'machined surface I56 in sliding contactwith a machined surface I57 provided at the outer side of a collar I58 extending upwardly from an adjusting'ring I59. The adjusting ring is supported on the top of thebullring and is provided around its outer.

periphery with teeth "I59 ior engagement with the teeth of pinion I40. The adjusting ring is also provided with a depending flange I6I by means of which it is axially positioned on the bull ring, the contacting surfaces of the flange and bull ring being suitably lubricated. The top ,surfaceof the adjusting ring collar I58 is also machined since this surface contacts thecover ring surface I50 in certain adjusted positions of the mantle. I

[The hull ring is retained in position by a plurality of retaining bolts I63 extending downwardly through the bull ring bosses I64 and the frame 1 flange I55. The head of each bolt IE3 is formed with a spherically" curved surface I56 disposed in in contact with the spherically curved top surfacesIB'I of a bronze washer !88 supported on one of the bull ring bosses I64. Each bolt is also encircled by a spring I69 which is interposedbetween the-frame flange I65 and a Washer 273, the latter being supported on the bolt by the-nut Ill. The springs I 69 provide suflicient resis ance to movement'of the bull ring under normal conditions but yield to permit movement of the ofthexnanhe lugs-I14. While the armssof theb s: extend pwardly throughcpeninss in the nt carrier and are. fi ted wi h nut llfiwhich be r against an underlying, Washer assembly supported in the mantle carrier, said assembly comprisn a resilient.rubberecanvas Wash r; Ill -con fined betweenunper and. lower metal plates I78.

when the crusher is in operation, the countershaftl24 should e rota-ted in a directipn 09pm site to the threadot the head iastening screw- I5 in order to prevent'loosening of the latter. Thus,

when screw 15 is a right hand thread thejcoun I tershaft Hisv rotated in an anti-clockwise direc tion hereby. caus he d shaft .0 to rotate' u a clockwise direction'when viewed in plan. Since adapter sleeve 82 islocked in place onpblique s aft exten o s. bythe pin 84, it i lowsth the a is '44 Qithe outer periphery of said sleeve willloe caused to yrateiin response tothe rotation orshaftii i, saida is d b ng an a inarycone havingits apex at thefocal point- 8i Whichisthe fQCus of eiyratingrmotion. -The roller bearing 92 is'thus actuated to. cause head liner 53.,andhead carrier 65 to oscillate on the sph al load; bearin surf ce Ma hs spherical rface 1 a 'o he. sk r portion o hehead carrier being also caused to move adjacent the spherical surface 43. Attention calledhere to thewedging action or" the crushing head- 'lddur ing itsoscillation on spherical surface it. As

It will also be seen thatthe inclination of the straight conical crushing surface. C, or". head l4 withfrei'erenc jto spherical surface ts i such thathead 14 functions asa wedge; the Wedging action of which varies with the position or the oc be gt ed and o e s n ef -"so t Ward the discharge zone. The general disposition of the mechanism eiiecting this wedging actionieature governs the selection or" the cone angle ofthe head. It willalso be apparent that the force behind the wedging action of the crushing surface 0 during its approach'tc-wai'd the.

crushing surface 78 of mantle iii, is mainly appliedby the anti-friction bearing 82.

As hereinbefore mentioned, the principalobject of this inventionis to develop mechanical motion that -will impose on tne inaterial-. to be crushed the secondary forces of shear, torsion, and bendingpitis therefore of; great importance at this stageof my specification tocarefully consider the action of rock reduction in this inachine. Consider thereforethe crusher under normal feed and operationwhenthe rock contacting. area is much greater at the discharge because of theieven distribution near the discharge, and

' there being'fifty per cent of the head making bull ring when uncrushable material is fed-into the, machine between the conical crushing head 14 and the conical mantle IlI.

The mantle Ill is positioned Withinthe mantle carrier by the slopingmantle surfaces I12 and the matching :surface I13 of the mantle carrier and. is retained in place by the mantlelugs'ild and :the U-boltl'lfi. Ashore shown the-.bight portion of each bolt I15 is'engaged' beneath one an approach toward the mantle. Then, the even distribution of the aggregate being sized at the discharge zone, acts to hold the freely rotatable crushing head iii opposite the area of -pressure on the mantle Ill It must be appreciated that this holding force is enormous (tl:.e actual machine-from which these patent drawings are made had a head thirty inches diameter) and plays anirnportant partinthe fast reduction of large ore enteringthe crushing zone and'such reductionisgdescribed herewith. Vi hen a largerock drops. to i s. position inthe Crushing e ts 5 a head 14 approachesit. then it is obvious that the surface of the headdoes not malienormal approach to the mantle surfacebutdoes move radially about focus 18L. This is a diiferential motion as respects the two surfaces of the head and mantle and which we herein term vertical differentiation and differs from direct impact.

This vertical differentiation is mechanical and positive.

that the obliquity of axis G4 (which is here 3 The complete stroke, from maximum v to minimum is performed in 180 degreesaof head shaft rotation, it is therefore at once apparent degrees) moves through an angle of 7 degrees about the focus 8!. It must be kept in-mind that the lower part of the head is rigidly held against rotation by the aggregate between the two crushing elements near the discharge zone,

and it is because of this fact that that portion of the head near the intake must move to accommodate this oblique motion; thus, when viewed in the horizontal plane of the drawing, a point on the upper part of the head at. the

widest intake opening, viz., a point a would not move toward a point 17 on the mantle onthe plane of the paper of the drawing, but the point a would have to move toward the observer to accommodate the motioncau'sed by the oblique axis MK. e specting thetwo surfacesofthe head i i and mantle i1! 'and varies in this instance from zero at the dischargezone to maximum at the intake zone. We herein term this motion a"horizon tal differentiation.

To further elucidate this motion, let it here be considered that'the crusher is running and empty and one large rock enters theintake and is nipped at the point abetween the crushin elements. Here the aforesaid vertical differentiation is still effective on the rock because it is mechanical and positive, but the point a on the head :4 would move on the plan'eof the paper of the drawing toward the point I) on the mantle l?! because such now the center of -maximum pressure and consequently thelower portion of the head lqwill move to accommodate the moticn caused by the oblique axis.

This is again a differential motion re- In this case' in the direction of the opposingwork face of the there is no horizontal differentiation imposed upon the rock being crushed, the discharge zone being empty, and therefore void of rock pressure againstthe mantle H l the head is free to move on its axis it an-d'thus to make a partial rotation about the center of pressure of thesolitary rock being crushed. f i he extra pressure and energy to breakdown a large rock under the last i mentioned conditions is easily detectable by the measure of shock present in the machine when these circumstances obtain.

The partial rotation above mentioned is always present as it is mechanical and therefore positive, and is generally combined with both the horizontal and vertical differentiationgaforemen tioned and produces torsion within the ro-ckbeing crushed. g

The bending stress above referred to'is the ec centric loading imposed upon the rock because As hereinbefore stated, one of the objectsof Y e V the invention is to produce a rock crusher that will perform a far greater reductionratiothan It is therefore of importance is at present'knownto the art. 7 To this end the crusher is designed so that the relationship between the position of the focal point Blythe.

amount of obliquity of the gyrating axislid and thecontour and cone angles. of the crushing members it and l H is such'tl'ia'tthe pointon the-crushing head which makes the closest ap proach to the mantle during e -crushing stroke does sowith a downward component ofmotion which is not less than five times and not greater than seven times the component of motion in the direction ofthe mantle; Inother words, the ratio betwe'enthe vertical and horizoiitilfdistances travelled by said point'in making its closest approach to the mantle 'during'a crushing stroke should be as represented by the following formula where X (Figs. 1 and '14) represents the'vertic'al distance traversed by that point P on thework face of the crushing head which, during a crush ing stroke, makes the closest approachto the opposing work face of the mantle; Y represents the distance through which said point P moves mantle during the. said crushing stroke; and

wvhere the value of Z is not less than Sand not greater than 7. 5

Fig. leis a: diagram illustrating one method of designing a=crusher so that the relationship between the. position'ofthe' focal point 8!, the

amount of obliquity (GB) of the gyrating axis it and the contours and cone angles of. the crushing members 14 and [ill issuch that. the point P'yon the crushing head-work face which makes the closest approach-to the mantle during a crushing stroke does so in such a way. that the ratio between the: vertical and horizontal dis tances' traversed by said point'is in accordance with the above mentioned formula. The dotted lines in Fig. 14 indicate the position assumed by :the crushing head 1.4 when it is rotated 180 from the position indicated byifull lines: r

In the layout illustratedin'Fig: .14 the angle of nip is indicated at N and is intended to I represent an angle of: 16: at mean obliquityset-' ting (2 /29) of the axis M? The obliquity or the axis id maybe varied from aminimum obliquity of 1 /2 to a maximurn' obliquity of 3 12? bYap- 'propriate adjustment of the previously mentioned adapter sleeve .82. The included angle M ofthe I the formula i mantle ii! is 54 and therincluded angle H of the crushing head M is 80. 1

' The crushing surfacefil. of the crushing head M comprises an upper portion C'of straight cone" contour 'and-aloweri curvedportion Vwhich is involute to an imaginary circular evolutc D whose, centre coincides with the focal point eLgThe' involute V is' of a greater degree of curvature in its lower'po'rtion' than in itsupper portion. The

point P is located on the curved portion V so that, when s-aid'point reaches its position of 0105- est approach tothe mantle crushing surfacel8, it lies on a normal R1, the lengthlof which is approximately six times the radius R of the 'evolute D. In this particular case the ratio of I fRi over R. is equalto approximately 6 and the ratio-between the verticaland horizontal distances travelled by the point P in makingits closest approach to the mantle is represented by It will now be shown that, when the position of the focal point 8| is changed so that the ratio 017R; over R equals some valueother than 6, there will be a resulting change in the ratio between the vertical and horizontal distances traversed by the point P in making its closest approach to the mantle; j i

As an example, the location of the focal point 8| shown in Fig. 15 issuch that the ratio of R1 v over R is assumed to equal 5, In this case the ratio between the vertical andhorizontal distances traversed bythe point P in making its closest approach to the mantle would be represented by the formula approximately. Similarly, the location of the focal point 8] shown in'Fig. 16 is'such that the ratio R1 over R is assumed to equal '7 using the radius R for the circular evolute D, In this case the ratios between the vertical and horizontal distances traversed by the point P in making its closest approach'to the mantle would be represented by theformula I 7 V i p X 7 As previously intimated, it is, an important' feature of this invention that the design of the crusher be such'that value of Z in the formula ra shall be not less than and not greater than 7. In otherwords, if the point P in making its closest approach to the mantle travels through a vertical distance which is less than five times or greater than seven times the horizontal distance traversed by said point the efficiency of the pressing action is impaired as compared with the case where the ratio between the vertical and horizontal distances travel-led by the point P in making its closest approach to the mantle is in accordance with the formula g inclusive.

To further clarify this vital relationship an 1 1 analogy (Fig. 17) may be used, to wit, a flat surface for the stationary and resisting work surface I8 while the moving member H is assumed to have a flat surface in one direction.

face GI is inclined with respect to surface it or a parallel thereto, said inclination being ap proximately 10 degrees from surface 18 The curve V ofsurface 'BI' is involute to an evolute D whose radius R, is approximately one sixth of'the length of normal R1; surface 5| .moves about the evolutecenter iii,

The entire receding 6 degrees, thus the surface 0 oscillates between 10? to 16 from surface 18", is well known, ifrock material be placed between'two'surf-aces making normal approach thelone to the other, thenan infinite amount of pressure, cannot make-those surfaces meet because thefriction of the expanding crushed rock against-its, confining surfaces, prevents further expansion of the rock thusret'ained in the center of pressure. If, however, a differentiation of said surfaces be effected in proper proportion with the pressure applied, then such action may continue until the surfaces meet.

In the other direction a flat surface portion C of sur- Referring therefore to Fig. 17- and which is analogous to the action of the crusher disclosed this invention, it can bedemonstrated that surface siste'd bythis bearing.

ifwhen in the position of nearest approach surface Bid meets surface i3 and surface 6} is 10 from surface s, that if these surfaces be resisted from movement except that member it may rotate about evolute center 8!, and that be receded 6 degrees, that average in hardnessdry rock beallowed to fall therebetween, 'sufiicient power can now be applied to seventieth of a-circle) isless than one half of one per cent. Thusthe substitution of an arc for the involute curve V isa feasible substitution within the scope 'of' this invention.

As is well known to the crushing art, different rocks and ores and other crushable ,materials vary widely in their friability and structure and the same results would not be obtained for each :kind in crusher of set characteristical have therefore incorporated intomy machine novel means for varying the obliquity of the gyrating axis, and at the sametime providing a unique and efficient method of applying the upperroller bearing cone 93a, andthis can be easily appreciated as a vital point in'thegeneral assembly seeing all resistance to prime motion must be re- Referring to 1, the adapter-sleeve 82 engages the taper shaft end We, being a jamming taper of!) degrees. The adapter 82 is-a slip fit in bearing cone SBafbut with pressure applied by nut 88 forcing'sleeve down"taper 19a the proper; amount of interference may be imposed against the cone b'ore to meet the manufacturers requirements for this type of service."

In assembl ing, thebearing cone S3 is placed on the surface "GiSQf-headliner 53, the adapter 82 and 'cone'93a are placed into position, care being taken :to see'that pin '84 engages'the 'desired notch 85 for theamount of obliquity required; shims 5::- are then placed on annular face 82-, next spherical washer 95 is positioned and nut 88 screwed-down with a predetermined degree of torque or effort, such effort being principally imposed against taper 79:: through sleeve ai -and shims S5.

With shaft 38 retained in its uppermost position by some exterior lifting force, and by the use or" a; suitable gaugethe'amount of clearance between cone Stand flat surface maybe determine-cl. If the clearance here is too great,

thenv a shim must be removed and nut 88 replaced. "It is important here to note the relationship existing between the nut 88, the washer 95, the cone 93a and the'a-dapter sleeve 82.

t is important to bear in mind at this stage 'tha'tthe adapter sleeve 82 was forced down the gripping taper 19a and has imposed an interference fit on the bore of cone 93a and which fit still exists even though the nut 83 is removed. The nut 83 is now'replaced and when the spherical face 85, the flat face of washer 95, and the cone face'meet, there will exist between the upper end of adapter 82 andthe extension-'81 of nut Q3, a space equal'to thethickness of the shim removed from shims 85.

The effort nowap'plied by the nut 88 will be first efiective in sliding the cone 93a along the axis 44' of adapter 82 to beiollowed by sufiicient effort to maintain a rigid assembly. The

above procedure can be followed until the desired The precise clearance adjustment is obtained. here required is ascertained from a formula furnished by the bearing manufacturers in conjunci tion with the interference fitof the cone $3- in;

the head carrier 58.

To vary. the obliquity of the gyrating axis 4 V as respects the vertical axis Me, the obliquity of the axes 34d and Mof the adapter sleeve 8?. is used to increase or decrease the-set obliquity of the head shaft axes 34d and Me. It is convenient to have this set obliquity of the head shaft 88twoand one-half degrees, and the obliquity of the axes of the adapter -82 one degree. As shown in Fig. 1, theobliquity of one degree of the adapter 82 is added to the obliquity of 2 /2 degrees of the axis 3 3d, thus making a total obliquity of 3% degrees. It is obvious that by rotatingthe adapter 82 180 degrees, theon'e degree of the adapter obliquity wouldbe subtracted from the shaft obliquity of 2 /2 degrees, thus mak- 7 ing the effective obliquity of the gyrating axis M one andone-half' degrees. Notches 85-01 I which there are five, as shown in Fig. 8,,would give increments of one-halfdegree'from aminimum of 1 /2 degrees to a maximum of degrees obliquity of the gyrating axis 44'; To effect-this 1 clamps I33 on the underside;-

lowered toits approximate'position. Turning cap screws -|35fwi11' cause the-clamps 133 to rise, thus raising threaded wedge segments l28, said"segments will therefore be confined byconta'ct with the threaded portion l-25 of mantle c'arrier' I22 on" the-inside; byv contact "with the slope of the conica1surface l3! onthe'cutsidef and the Itshoi'ild be noted that'th upwar'd cr'ushing' forces imposed on the mantle ill assisttomainjtai'n intimate contact between the bull ring v 'I l E} .andthe mantle carrier I22, dueto the wedging action of wedge segments !29.'- j Y 'Whenit is necessary to make. an adjustment of the crusher'spac'e s for-product size; the cap screws I35 areslackened' about one-half turn each with a suitable wrench andthenfwi'th the same wrench, which fits the square section'o'n the v top portion of pi nions sleeye M2, the turni'ngof change of adjustment, his only necessary to remove the head carrier 58, remove the nut 88, withdraw the adapter 82 sufficiently to rotate said sleeve to the required adjustment and then to tighten nut 88 to it's original position, suitable indicating figures '(not shown) being stamped on top surfaces of the nut and head shaft for this precise purpose.

The exclusion of dust from the means of adjustment in gyratory crushers usually'involves 'the use of auxiliary component parts such as !22 are of one diameter and are machined-for Due to tltds free fit within the bull ring H9; construction it is entirely unnecessary: taprovide auxiliary pieces to hold the packing I2! or to provide a cylindrical shield as sealsmediuin, the bull ring Ht offering a rigid, integral cylin drical sealing surface I29.

The satisfactory seal arrangement-above menof the movable threaded wedge segments i29 and which are adapted to be closed in on the threaded portion I25 of mantle carrier 122. This move ment of the threaded Wedgesegments i2 5 is, ac-

complished in the following manner: Before entering the mantle carrier E22 into the bull ring H8, the cap screws 135 are slackened. to permit the clamps I33 to drop tothe chain line position shown in Fig. 1, thus permitting the wedge segments I29 to likewise lower accordingly. "Due to the cone angle of the surfaces island l32'wedge "said-"pinion M0 will-'rotate th adjustingfring l59,';which,-=in turn, will }rotate the mantl 'car- Theicoarse pitchthread 25 will quickly bring the mantle-carrier assembly to the desired posi- *tion,: when it is only-necessaryfm tighten the -clapscrews 135.

lockin-gar'rangement in-service. The adjustment hereindescribed can be carried out by two op- Thi has proved af very rigid erato rsg i'f desired, by providing pinions Hill 'at opposite sidesof thebull ring H9; 1 Y

'f IX 'i gyratory crusher's" where all 'fthe operating mechanism is under the crushing zone S, the im- .j po rtancev of separating the dust'l'aden' air without, fromthe load bearing lubricated surfaces.

within, is at once apparent and cannot befover stressed; This importantfunction iseffectu'ally' j solved in the case of my'invention by'placing the oil seal ringed in .Shlfink fita-bout the parall'elcylindricalpo-rtion46. It' will'be obseryedthat 'whenthe bottom edge of head liner '53'is in'its.

uppermost"pos ition, it is still well below the top edge of the oilseal ringdfl and ate distance'from it, thus, oil adhering to the said bottom edge of i head liner ssga d' oscillating at, 400- RIP. M. in

an ar'c about the focus 8!, istrappe'd by the oil seal ring 48-and co-mpl'etelyretained within-its proper limits.- 1 I I The spherical sphere head 49. These surfaces l2a-and43 'are dry and without-lubricant and are effective to:

-- prevent'the' passage ofdust ladenair from-entering the annular space m. This arrangement acts as a breather or vent to the otherwise airtight chamber containing the lubricated working parts "of the'machine, the expanding-or contracting air within the confined chamberhaving free pastioned-is made possible by the novel arrangement sage-through'hcles 5E. and thence. over the 'oil seal ring tsand through theventspace at the spherical. area-43. iThus'a triple purpose is served'by this novel arrangement, to wit: an oil-seal, adust seal and as vent; each ofwhich functions are efiectually performed in service.

As previously stated, the excess oilpassing re.-

lief valve 69 serves to lubricate the pump drive spiral gear 32 and' the countershaft bearings 25 and 2?, said oildraini'ng off-into sump?! in bot- Ti) tom cover Hi throughoutlettii, thenceto filtering tankinotshown),

segments it may now recede radially sufiicient- 1y to clear the mantle carrier i22, which is now?" 1 1. A gyratorycrusher oi the coiie andm'antlel. type comprisingi .cone and mantlefelements of substantially trusts-conical form, said elements surfaceiila provided adjacent the lower edge of the skirt portion Wei-head car- *rier E3ispositionedclos'ely adjacent but'not inactual contact-with the spherical surface 43 of vided ln'the lower end of the adapter sleeve.

g 5. -A gyratory crusher as set forth in claim 1 being relatively inclined so that theircentralaxes meet at a focalpoint. locatedbelowa crushing zone formed :by and; between their opposing crushing surfaces, and means f rgyrating-the 'cone, element aboutsaid focal point, said means 7 comprising a driven shaft includinga main shaft er sleeve fitted-on said shaft extension and an 7 antifriction bearing interposed between a portion of the cone element and said adapter sleeve, the axis of the bore of said sleeve coinciding with the axis of said shaft extension and being obliquely 7 inclined with respect to the axis of the outer periphery of the sleeve, the last mentionedaxis coinciding with the central axisof the cone element, said sleeve being adjustable about said shaft extension and means for securing the sleeve in adjusted position. i V I 2- A gyratory crusher as set forth in claim 1 in i which the means for securing the adapter sleeve in adjusted position comprises a pin fixed to the shaft and projecting into one of a series of pin receiving recesse formed in the sleeve.

3. A gyratory crushe'r'as set forth in claim 1 inwhich the shaft extension andthe bore of the adapter sleeve are tapered to provide a jamming fit therebetween.

4. A gyratory crusher as setforth in claim 1 including a nut threaded on the end of the shaft extension toexert pressure'against the adjacent 'uppe'r endof the adapter sleeve, and a pin fixed to the main section of theshaft and projecting into one of a series of pin receiving recesses proin which the shaft extension 'andthe bore of the sleeve are tapered to provide a jamming fittherebetween and in which thesleeve is forced into tight jamming engagement withnthe taperedv r shaft extension by means-of a pressure applying nut threaded on. the upper end ofsaid extension and bearing against the upper end-"of the sleeve. 6. A gyratory crusher asset forth in claim; 1

including an inner race member encircling said;

sleeve andforming part of said anti-friction bearing a pressure applyin nutthreaded on the upper end of said shaft extension, shims interposed between a lower portion of said nut and the adjacent upper end of the adapter'sleeve, and a washer interposed between another portion of the nut and the upper end of said inner race memher, said washer. and-nut being provided with spherically curved bearing surfaces curved about a centre lying below saidsurfaces. l 7. A gyratory crusher of the cone and man-V tle type comprising afram'e, a mantle element,

. means mounting said mantle element on said framefso that the central axis of the mantle element is vertical, a cone element arranged within said mantle element and constituting a crushing head, a support on which the cone element is mounted in atilted position sothat the central .axes of the mantle and cone elements are relatively inclined to meet at a focal point located below acrushing zone formed by and between the opposing crushing surfaces of said; elements, a

cone driving shaft including a main section and an. obliquely inclined shaft extension, the main shaftsection being journalled so that itscentral axis coincides with the central axis of the mantle element and meets thecentral axis of the inclined shaft extension at said focalpoint, and means for journalling said inclined shaft extension in the cone element' said means includin a tilt-adjustelement which is adjustable to vary the extent to which the cone element is tilted.

8. Agyratory crusherof the cone and mantle type comprisin v a frame, a mantle element, means mounting said mantle element on said frame so that the central axis of the mantle ele- Iment is vertical, a cone element arranged Within said mantle element and constitutinga crushing head, a support on which the cone elementl-is mounted in a tilted position so that the central axes of the mantle and cone elements are relativelyinclined to meet at a focal point located below a crushing zone formed by and between the opposing crushing surfaces of said elements, a cone driving shaft including a main section and an obliquely inclined shaft extensiomthe main shaft section being journalled so that its central axis coincides with the central axis of the mantle element and meets the central axis of the inclined shaft extension at said focal point, and means for journalling said inclined's haft extension in the cone element said means comprising an adapter sleevefitted on said shaft extension and a bearin assembly interposed between a portion of the cone element and said adapter sleeve,. the axis of the bore'of said'sleeve coinciding with the axis of said shaft extension and beingobliquely inclinedwith respect to theaxis of the outer periphery of the sleeve, thelastmentioned axis coinciding with the central axis of the cone element, saidsleeve being adjustable about said shaft extension'and meansfor securing the sleeve in adjusted position.

9. 'A gyratory crusher of the cone and mantle type comprising cone and} mantle elements of substantially,frusto-conical form, said elements being relatively inclined so that their central axes meet at a focal point located below the crushing zone formed by and between their opposing crushin surfaces, and 'means for ,gyrating the cone element about said focal point so that, at

. each crushing stroke, the portionrof the active crushing surface of the cone element which makes the closest approach to the opposing crushing surface of the mantle does so with a substantial downward'component of motion, said crusher being further characterized in. that the V crushing surface of the mantle, as viewed in vertical cross section, is of straight cone contour while the'opposing crushingsurface of the cone element, as viewed in vertical cross section, comprises an upper portion of straight cone contour and a lower curved portion which is involute to an imaginary circular evolute whose centre coincides with said focal point and whose radius is approximately one-sixth the length of its normal which is perpendicular to the crushing surface of the mantle, said straight cone contour portion of r the coneelement being tangent to said involute curved portion and the latter being tangent to either the mantle crushing surface or a parallel thereto and being also of a greater degree of curvature in its lower portion than in its upper portion.

10. A gyratory crusher of the cone and mantle type comprising cone and mantle. elements of substantially frusto-conical form, said elements being relatively inclined so that their central axes meet at a focal. point locatedbelow the crushing 'zone formed byand between their opposing crushing'surfaces, and means for gyrating the cone element about said focal point so that, at each crushing stroke, the portion of the active crushing surfaceof the cone element which makes the closest approach to the opposing crushing surface of the mantle does so with a substantial downward component of motion, said crusher'being further characterized in that the crushing surface of the mantle, as viewed in vertical cross section, is of straight cone contour while the opposing crushing surface of the cone element, as viewed in vertical cross section, comprises an upper portion of straight cone contour merging with a lower portion which is curved so that,

when said lower portion is making its closest approach to the mantle, the point on the arc of curvature which is nearest the mantle is located on a radius which is perpendicular to the crushing surface of the mantle and substantially tangential to an imaginary circle whose centre coincides with said focal pcint'and whose radius is approximately one-sixth the length of the first 7 mentioned radius. 7

11. A gyratory crusher of the cone and mantle type comprising a frame, a mantle element of 7 said frame so that itscentralaxis is vertical, a 1 gyratory cone element of substantially frustoconical form arranged within said mantle element, said frame and cone elements being provided with spherically curved bearing surfaces in I contact with each other said cone'element being tilted so that its central axis meets the central axis of the mantle element at a focal point which constitutes the center of curvature of'said spherically curved surfaces and is located below the crushing zone formedby and between the oppos- .ing crushing surfaces of said-cone and mantle 7 elements, one of said spherically curved surfaces 7 from said groove, said last mentioned means including an oil pressure regulating valve, and means for gyrating said cone element about said focal point.

RAYMOND E. BROWNING.

substantially frusto-conical form mounted on 

